EP0411913A1 - Assemblage d'un piston pour un moteur de combustion interne - Google Patents

Assemblage d'un piston pour un moteur de combustion interne Download PDF

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Publication number
EP0411913A1
EP0411913A1 EP90308443A EP90308443A EP0411913A1 EP 0411913 A1 EP0411913 A1 EP 0411913A1 EP 90308443 A EP90308443 A EP 90308443A EP 90308443 A EP90308443 A EP 90308443A EP 0411913 A1 EP0411913 A1 EP 0411913A1
Authority
EP
European Patent Office
Prior art keywords
compression ring
land
piston assembly
chamfered surface
gap
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP90308443A
Other languages
German (de)
English (en)
Other versions
EP0411913B2 (fr
EP0411913B1 (fr
Inventor
Takayuki Arai
Takaharu Goto
Kyugo Hamai
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Publication of EP0411913A1 publication Critical patent/EP0411913A1/fr
Application granted granted Critical
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Publication of EP0411913B2 publication Critical patent/EP0411913B2/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/04—Thermal properties
    • F05C2251/042—Expansivity

Definitions

  • This invention relates to a piston assembly of an internal combustion engine by which oil consumption is improved under a high load condition of the engine and under a negative pressure condition in a combustion chamber.
  • Fig. 8 of the present application One of the compression rings is shown in Fig. 8 of the present application and disclosed, for example, in Japanese Utility Model Provisional Publication No. 59-126158. Another is shown in Fig. 9 of the present application and disclosed, for example, in Japanese Patent Provisional Publication No. 62-251457.
  • a compression ring 10 is so arranged that its opposite end sections partially overlap each other.
  • One end section of the compression ring 10 has a recess 14 in a corner formed by an outer periphery 11, an upper surface 12, and an end surface 13.
  • the upper surface 12 is on the side of a combustion chamber.
  • the other end section of the compression ring 10 has a projection 5 which extends to the one end section to lie upon the recess 14 in a manner to be in tight contact with the surface of the recess 14.
  • a compression ring 16 has opposite end surfaces 17.
  • a lower section of each end surface 17 is chamfered by machining to form a chamfered surface, so that the compression ring 16 has a clearance C4 between opposite upper sections of its end surfaces 17 and a clearance C5 larger than the clearance C4 between opposite lower edges of the chamfered surface.
  • the present invention provides a piston assembly comprising a piston which includes a top land formed at an upper part thereof.
  • the top land has a first chamfered surface at a lower peripheral edge thereof.
  • a second land is formed under the top land and has a second chamfered surface at an upper peripheral edge thereof.
  • the second chamfered surface has a width larger than that of the first chamfered surface.
  • the top and second lands defines a compression ring groove therebetween.
  • a compression ring is disposed in the ring groove to be slidably contacted with the cylinder.
  • the compression ring has opposite ends surfaces defining a gap.
  • the piston assembly P comprises a piston 6 having a compression ring 2 and an oil ring 4.
  • the compression ring 2 is disposed in a compression ring groove 2a formed between a top land 1 and a second land 3 of the piston 6.
  • the oil ring 4 is disposed in an oil ring groove 4a formed between the second land 3 and a shoulder section 4b of a piston skirt 6a.
  • a lower peripheral edge of the top land 1 is chamfered by machining to form a chamfered surface 1a having a width C1′ (in Fig. 1C) not larger than 0.1 mm.
  • the width C1′ is as small as possible.
  • the chamfered surface 1a extends annularly along the outer periphery of the piston 6.
  • An upper peripheral edge of the second land 3 is chamfered by machining to form a chamfered surface 3a.
  • the chamfered surface 3a extends annularly along the outer periphery of the piston 6.
  • the width C1 (in Fig. 4A) of the chamfered surface 3a is set at a predetermined value so that a pressure in a space formed between the second land 3 and the wall of a cylinder 5 becomes larger than a predetermined level.
  • the wall of the cylinder 5 may be part of a cylinder liner. Therefore, the chamfered surface 1a of the top land 1 is formed smaller in width than the chamfered surface 3a of the second land 3.
  • the compression ring 1 has a butt-type piston ring gap C.
  • the opposite end surfaces 2s of the compression ring 2 are flat and perpendicular to an axis of the ring 2.
  • the end surfaces 2s are parallel with each other and spaced from each other to form the gap C.
  • the gap C is determined to be as small as possible within a range to prevent a contact of the end surfaces 2s due to thermal expansion under engine operation.
  • a reference numeral C1 indicates the width of the chamfered surface 3a.
  • a clearance C2 is a distance between the wall of the cylinder 5 and the peripheral surface of the second land 3.
  • the cross-sectional area S1 is defined by the gap C and a clearance C3 which equals to the total of the clearance C2 and the clearance C1. Therefore, the cross-sectional area S1 equals to C x C3.
  • the cross sectional area S2 is generally defined by the gap C and the clearance C2, and generally equals to C x C2. Strictly speaking, the clearance C2 in Fig.
  • 5A is a clearance C2′ which is the total of the clearance C2 and the width C1′ of the chamfered surface as shown in Fig. 1C.
  • the clearance C2′ generally equals to the clearance C2, so that the cross sectional area S2 may be defined by the clearance C2 and the gap C.
  • FIG. 3 there are shown changes in oil consumption amount (the amount of lubricating oil consumed in the combustion chamber) under high and negative pressure conditions in the combustion chamber when the cross-sectional areas S1 and S2 are changed by a change of the gap C.
  • a line L1 represents the change in the oil consumption amount under a high pressure condition in the combustion chamber such as during a high load operation of the engine. The line L1 indicates the fact that the oil consumption amount decreases with an increase in the cross-sectional area S1.
  • a line L2 represents the change in the oil consumption amount under a negative pressure condition in the combustion chamber such as during an engine-brake operation. The line L2 indicates the fact that the oil consumption amount increases with an increase in the cross-sectional area S2.
  • the cross-sectional area S1 is as large as possible whereas the cross-sectional area S2 is as small as possible.
  • the gap C of the compression ring 2 is set at a minimum size within the range to prevent a contact of the end surfaces 2c due to thermal expansion under a driving condition of the engine.
  • the gap C is set at 0.2 mm for a compression ring used on a piston having a bore diameter of 83 mm.
  • the chamfered surface 1a of the top land 1 is machined so that the width C1′ of the chamfered surface 1a is not larger than 0.1 mm. Therefore, the cross-sectional area S2 is made very small, so that the oil consumption is suppressed under a negative pressure condition.
  • the cross-sectional area S2 is defined by the gap C and the clearance C2 while the cross-sectional area S1 is defined by the gap C and the clearance C3.
  • the cross-sectional area S1 includes a cross-sectional area S1′ which is defined by the gap C and the chamfered surface width C1 and equals C1 x C, so that the cross-sectional area S1 equals the total of the cross-sectional area S2 and the cross-sectional area S1′. Therefore, the cross-sectional area S1 can be enlarged, so that the oil consumption is suppressed under a high pressure condition of the combustion chamber.
  • the chamfered surface width C1 of the peripheral upper edge of the second land 3 is determined according to the graph of Fig. 6 so that the pressure in a second land space 3b defined by the second land 3 and the wall of the cylinder 5 becomes not lower than 0.18 MPa.
  • the graph of Fig. 6 is cited from a technical article "Sealing Performance of Two Rings Piston" in the transactions of the Society of Automotive Engineers of Japan Inc,. published on April 25, 1988.
  • S2 is determined by the amount of the oil consumption under a negative pressure condition.
  • the width of the chamfered surface 3a is determined at a predetermined value with which the above-described equation (4) is satisfied.
  • the oil hardly stays at the end section 2s in this arrangement, the oil consumption can be suppressed without minimizing the oil blow-down force by the blow-by gas cannot be minimized so that oil consumption is suppressed.
  • a character Za indicates a zone where an oil consumption is permittable under a high pressure condition in the combustion chamber.
  • a character Zb indicates a zone where an oil consumption is permittable under a negative pressure condition in the combustion chamber.
  • a character Zc indicates a zone common between the zone Za and the zone Zb. Thus, in the zone Zc, the oil consumption is permittable or sufficiently suppressed under the high pressure and negative pressure conditions in the combustion chamber.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
EP90308443A 1989-07-31 1990-07-31 Assemblage d'un piston pour un moteur de combustion interne Expired - Lifetime EP0411913B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP196944/89 1989-07-31
JP1196944A JPH0364654A (ja) 1989-07-31 1989-07-31 内燃機関用ピストン

Publications (3)

Publication Number Publication Date
EP0411913A1 true EP0411913A1 (fr) 1991-02-06
EP0411913B1 EP0411913B1 (fr) 1993-04-28
EP0411913B2 EP0411913B2 (fr) 1995-12-20

Family

ID=16366255

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90308443A Expired - Lifetime EP0411913B2 (fr) 1989-07-31 1990-07-31 Assemblage d'un piston pour un moteur de combustion interne

Country Status (4)

Country Link
US (1) US5035210A (fr)
EP (1) EP0411913B2 (fr)
JP (1) JPH0364654A (fr)
DE (1) DE69001467T2 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09280053A (ja) * 1996-04-16 1997-10-28 Kioritz Corp ２サイクルエンジン
AT4877U1 (de) * 2000-08-24 2001-12-27 Avl List Gmbh Kolben für eine viertakt-brennkraftmaschine
DE10311155A1 (de) * 2003-03-14 2004-09-23 Gapi Technische Produkte Gmbh Dichtring und Dichtringanordnung
US6935220B2 (en) * 2003-05-30 2005-08-30 Bendix Commercial Vehicle Systems, Llc Contoured piston
US10753310B2 (en) 2012-02-10 2020-08-25 Tenneco Inc. Piston with enhanced cooling gallery
BR112016002673A2 (pt) * 2013-08-07 2017-08-01 Federal Mogul Corp anel de pistão
GB201319087D0 (en) 2013-10-29 2013-12-11 Indian Ocean Medical Inc Artificial airway device
JP6695663B2 (ja) * 2015-07-09 2020-05-20 株式会社リケン 内燃機関用のピストンリング
US10030604B2 (en) 2016-07-29 2018-07-24 Caterpillar Inc. Piston top land structure

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR94125E (fr) * 1967-02-17 1969-07-04 Geffroy Robert Ensemble piston et segments pour moteur a combustion interne.
US4253435A (en) * 1979-02-26 1981-03-03 International Harvester Company Diesel engine and piston assembly therefor
US4848212A (en) * 1986-04-24 1989-07-18 Mazda Motor Corporation Internal combustion engine piston with two compression rings having reduced oil consumption

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3862480A (en) * 1971-11-05 1975-01-28 Int Harvester Co Ring manufacture, productive of face contact seal
US4079661A (en) * 1976-06-04 1978-03-21 Caterpillar Tractor Co. Piston construction
US4193179A (en) * 1977-11-14 1980-03-18 Condor Manufacturing Inc. Process of manufacturing an article having a groove rolled therein, and an article produced thereby
GB8622538D0 (en) * 1986-09-18 1986-10-22 Ae Plc Pistons

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR94125E (fr) * 1967-02-17 1969-07-04 Geffroy Robert Ensemble piston et segments pour moteur a combustion interne.
US4253435A (en) * 1979-02-26 1981-03-03 International Harvester Company Diesel engine and piston assembly therefor
US4848212A (en) * 1986-04-24 1989-07-18 Mazda Motor Corporation Internal combustion engine piston with two compression rings having reduced oil consumption

Also Published As

Publication number Publication date
JPH0364654A (ja) 1991-03-20
DE69001467D1 (de) 1993-06-03
US5035210A (en) 1991-07-30
DE69001467T2 (de) 1993-11-11
EP0411913B2 (fr) 1995-12-20
EP0411913B1 (fr) 1993-04-28

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